Method and apparatus for the control of air flows and pressures in air-conditioning
An object of the invention is a method and apparatus for the control of the fresh-air, input-air, exhaust-air, waste-air and return-air flows, as well as of the air pressure in the input-air duct and the air pressure in the exhaust-air duct, in an air-conditioning system in which the closing and control mechanisms for the fresh air and fresh-air bypass in relation to the heat recovery exchanger are coupled to each other as an intake-air mechanism and, respectively, the closing and control mechanisms for the exhaust air and return air are coupled to each other as an outlet-air mechanism. 
     There are two basic types of air-conditioning systems: constant-flow systems and flow-rate controllable systems. The constant-flow systems usually have one or two different operating rates, typically 1/1 rate and 1/2 rate. 
     In the constant-flow systems, the air flow is not regulated at all after a certain basic setting. For this reason the air flow will change during use as the filters of the air-conditioning system become soiled, as the heating radiator becomes soiled owing to the oil condensed on the cooling radiator, and as the heat recovery exchanger freezes. The air flow will also change owing to, for example, the thermal forces caused in the air-conditioning ducts by the temperature difference between the fresh air and the inside air, or by wind. Also, the air flow in a constant-flow system is not adjusted according to pressure changes in the duct system. Thus the air flows of the air-conditioning plant vary depending on the season of the year, the condition of the filters, and the shape of the characteristic curves of the fans and the duct system. The fresh-air flow and the waste-air flow vary independently of each other. 
     Flow-rate controllable systems are nowadays always connected with a flow-rate controllable air-conditioning system. The objective of the control is to maintain a constant pressure in the ducts. The pressure in the duct system is measured, and on the basis of this measurement the air flow in the air-conditioning plant is adjusted according to need. The fresh-air flow and the waste-air flow in the air-conditioning system vary independently of each other. 
     The air flows in present-day air-conditioning systems change readily when, for example, the filters become soiled or the heat recovery device freezes. The fresh-air flow and the waste-air flow change independently of each other, whereupon the pressure relations between the different parts of the building will change. The greatest disadvantage is undoubtedly the changing of the fresh-air flow and the waste-air flow independently of each other. As a consequence of this, humidity present in the indoor air in the building may condense on windows and structures, causing structural damage. Furthermore, spreading of odors around the building and drafts may also result. 
     By the method according to an embodiment of the invention, a crucial remedy is obtained for the disadvantages described above. In order to achieve this, the method according to an embodiment the invention is characterized in that the control of fresh-air, input-air, exhaust-air, waste-air and return-air flows (A, B, C, D and E, respectively) and of pressure in an input-air duct and of pressure in an exhaust-air duct are interconnected in such a way that a deviation from a predetermined value in one of these will cause a change of predetermined values in the others so that the difference (A-D) between the fresh-air flow and the waste-air flow, or their ratio (A/D), will change in a predetermined way. The apparatus according to an embodiment of the invention is characterized in that fresh-air flow and input-air flow meters and an input-air duct air pressure meter are connected to an input-air flow control and a waste-air flow meter and an exhaust-air duct air pressure meter are connected to a waste-air flow control, and that these control work together and are fitted to act on fans and outlet-air and intake-air mechanisms so that a change in one of the quantities measured will cause an adjustment of the input-air flow (B), the waste-flow (D), the outlet air mechanism and/or the intake-air mechanism so that ratio (A/B) of the fresh-air flow to the input-air flow and/or the difference (A-D) between the fresh-air flow and the waste-air flow, or their ratio (A/D), will be at the predetermined values and/or that a fresh-air bypass flow (F) will open or close. 
     It can be regarded as the most important advantage of an embodiment of the invention that the fresh-air flow and the waste-air flow in the air-conditioning system can be controlled (adjusted or maintained constant) continuously and independently of each other. In addition, in the air-conditioning system according to an embodiment of the invention, the controls of the pressure in the input-air duct and the pressure in the exhaust-air duct are dependent both on each other and on the fresh-air flow and the waste-air flow. It is a further advantage that the system is simple in construction. 
    
    
     The invention is described below in detail, with reference to the accompanying drawing. 
     FIG. 1 is a schematic representation of air-conditioning plant in which the system according to an embodiment the invention has been installed. 
     FIG. 2 depicts partially sectional side and plan views of an embodiment of a control and closing device. FIGS. 3-6 depict the application of the embodiment depicted in FIG. 2 as a control and closing device of an air-conditioning plant, in the various states of operation of the device. 
     The indications of the air flows are as follows: A is the fresh-air flow, B is the input-air flow, C is the exhaust-air flow, D is the waste-air flow, E is the return-air flow, F is the fresh-air bypass flow of the heat recovery exchanger, A&#39; is the fresh-air flow entering the heat recovery exchanger. 
     The input-air side of an air-conditioning system often includes, for example, the following parts: a fresh-air filter 2 in the fresh-air duct 21; the closing and control mechanisms of the fresh-air bypass, coupled to each other as an intake-air mechanism 3; a heat recovery exchanger 4; an input-air fan 5, an input-air flow meter 6, an input-air pressure meter 12 in the input-air duct 1; a fresh-air flow meter 15; and various air-treatment devices such as a heating radiator, a cooling radiator, an air-humidifier, air filters 7, 8, etc., which may be located at different points on the input-air side of the air-conditioning system. Typically the input-air flow B in the duct 1 is equal to the fresh-air flow A in the duct 21. 
     The exhaust-air side of air-conditioning system often includes, for example, an exhaust-air filter 16 and an exhaust-air pressure meter 19 in the exhaust-air duct 9, exhaust-air and return-air closing and control mechanisms coupled to each other as an outlet-air mechanism 10, and a waste-air fan 11 and a waste-air flow meter 20 in the waste-air duct 22. Typically the exhaust-air flow C in the duct 9 is equal to the waste-air flow D in the duct 22. 
     The input-air fan 5, the intake-air mechanism 3 and the outlet-air mechanism 10 are regulated by control 13, and the waste-air fan 18 by control 14. The input-air flow meter 6, the input-air pressure meter 12, and the fresh-air flow meter 15 are connected to control 13, and the exhaust-air pressure meter 19 and the waste-air flow meter 20 are connected to control 14. In addition, controls 13 and 14 are connected to each other. The intake-air mechanism 3 and the outlet-air mechanism 10, linked with the heat recovery exchanger 4, are preferably of the construction discussed below with reference to FIGS. 2-6. 
     When the flow resistance on the input-air side 1 of the air-conditioning system for some reason increases, for example as the air filter becomes soiled, the air flow will decrease unless the input-air fan 5 is correspondingly controlled or unless the flow resistance of the input-air side is otherwise reduced correspondingly. The input-air fan 5 and the input-air flow control means 17 can be controlled by control 13 on the basis of either air-flow measurement 6 or pressure measurement 12. The measuring and the control are so arranged that an adjustment of the input-air fan 5 or of the input-air control means 17 will compensate precisely for the error caused by the disturbance factor. In terms of control technology, the basis for this compensation is either the difference A-D between the fresh-air flow and the waste-air flow or their ratio A/D; either one of these, or both of them in alternation, or a value somewhere between them is maintained either constant or at a predetermined level by control 13. When the air flow has, under the effect of the above-mentioned adjustment, reached its limit value, the decreasing of the input-air flow will continue as the air filter continues to become further soiled. At this time the control 13 of the input-air fan, in accordance with the invention, will control the control 14 of the waste-air fan and/or of the waste-air flow control means 18 in such a way that the predetermined difference or ratio of the input-air flow B and the exhaust-air flow C will remain constant, which is essential with respect to the air-conditioned indoor space. Since, when the return-air flow E is closed, the input-air flow B is at all times precisely equal to the fresh-air flow A, this also corresponds to the maintaining of the difference A-D between the fresh-air flow and the waste-air flow, or their ratio A/D, at the predetermined level. 
     The operation is similar if the flow resistance on the exhaust-air side 9 in the air-conditioning system for some reason increases, for example when the exhaust-air filter 16 becomes soiled, the heat recovery exchanger 4 freezes, the fire damper of the air duct system is triggered, etc. In such a case the control 14 of the waste-air fan or/and of the control means 18 of the waste-air flow will control the control 13 of the input-air fan or of the control means 17 of the input-air flow in such a way that the difference A-D between the fresh-air flow A and the waste-air flow D, or their ratio A/D, or a value somewhere between them will remain constant or at the predetermined value. 
     When the waste-air flow D decreases to a value lower than the predetermined value, and the outside temperature is at the same time lower than the predetermined value, the intake-air mechanism 3 adjusts to a position in which the fresh-air flow A in its entirety is fresh-air bypass flow F, i.e. the fresh-air flow A&#39; through the heat recovery exchanger is cut off. As a consequence of this, the waste-air flow begins to thaw the heat recovery exchanger 4, if this has frozen. When the waste-air flow has risen back to its predetermined value and/or the predetermined time has elapsed from the cutting off of the air-flow A&#39;, the intake-air mechanism 3 will switch back to its initial position, in which there is no fresh-air bypass flow F. This chain of steps can be repeated a predetermined number of times, typically 2-3 times. If the waste-air flow has not thereby risen back to its predetermined value, an alarm signal of an error operation will be given. 
     When it is desired to change the fresh-air flow A to be smaller than the input-air flow B, and a predetermined (ratio A/B is desired as their ratio, part of the exhaust-air flow C is directed by means of the outlet-air mechanism 10 as a return-air flow E to serve as input air B. In this case, after a changing of the position of the outlet-air mechanism 10, the input-air flow B or the pressure in the input-air duct 1 is adjusted to a predetermined value. Thereafter the waste-air fan 11 or the waste-air flow control means 18 is adjusted so that the difference A-D between the measured values of the fresh-air flow and the waste-air flow, or their ratio A/D, will become the predetermined constant value. If thereafter the input-air flow B or the pressure in the input-air duct 1 does not deviate from the predetermined value by more than a predetermined value, the ratio A/B of the fresh-air flow to the input-air flow will be compared to the predetermined ratio. This chain of steps is repeated in the order presented, or in part, until the input-air flow B, the ratio A/B of the fresh-air flow to the input-air flow and at the same time the difference A-D between the fresh-air flow and the waste-air flow, or their ratio A/D, reach their predetermined values. Thus the outlet-air mechanism 10 and thereby the return-air flow E may be for the control steps a starting point which has first been set according to other criteria, or alternatively the outlet-air mechanism can be used as a control means for achieving the desired fresh-air to input-air ratio A/B. 
     In the event that the apparatus is simpler in construction in such a way that it does not include the possibility of using a return-air flow E, in which case the exhaust-air flow C is at all times equal to the waste-air flow D, the control method will be simply to control the flows directly in the input-air duct 1 and the waste-air duct 22 in order to control the input-air flow B or/and the waste-air flow D, while keeping, however, the said difference A-D between the fresh-air flow and the waste-air flow, or their ratio A/D, as the criterion. 
     In principle the method described above can be applied by using components of any type, but preferably both the intake-air mechanism 3 and the outlet-air mechanism 10 are fixed to the heat recovery exchanger 4. Preferably in these mechanisms the closing and control means, such as levers or similar means, are coupled to each other in such a way that, in the outlet-air mechanism 10, a gradual closing of the waste-air flow D will cause a simultaneous gradual opening of the return-air flow E at a corresponding rate, and vice versa, and, in the intake-air mechanism 3, the closing of the fresh-air flow A&#39; to the heat recovery exchanger 4 will cause a simultaneous opening of the fresh-air bypass flow F, and vice versa. It is also advantageous, in order to obtain a reliable measurement, that the input-air and waste-air flows A, D are measured in the pressure apertures of the fans 5, 18, or in the continuations of the apertures. Furthermore, it is preferable to measure the fresh-air flow at the point of connection of the air-conditioning system to the fresh-air duct or inside the air-conditioning system at a point before the filter or after the filter in the direction of the air flow, and that the pressures of the input air and exhaust air B, C are measured inside the air-conditioning system or at the points of connection of the air-conditioning system to the input-air and exhaust-air ducts 1, 9, inside the system. 
    
    
     As mentioned above, the control and closing mechanisms of the fresh-air bypass are coupled to each other as an intake-air mechanism 3 and the exhaust-air and return-air closing and control mechanisms are coupled to each other as an outlet-air mechanism 10. An example of such a control and closing mechanism is illustrated in FIGS. 2-6. The mechanism shown in FIGS. 2-6 has two or more control dampers 31a-c, 38, intended for the control of gas flows and interconnected by means of levers 33, the angle between the fully open and the fully closed positions of the dampers being G or H, which is preferably 45°. The control dampers 31a-c, 38 may in total move over an angle of 2A, since in this case angle A=angle B, i.e., preferably 90°, in which case the position of the dampers is shifted from the first fully closed position 39 via the fully open position 40 to the other fully closed position 41. 
     The embodiment of FIG. 2 thus has a total of four control ducts for air flows 37a-c and 42, the ducts being in this case separated from one another by partitions 43 and from the exterior by end walls 44 and a side walls 45. The air flows travel through the device in parallel and under the control of the duct side walls 45 and partitions 43 or, respectively the end walls 44. Each control duct thus has preferably one control damper 31a-c or 38, which in the fully open position is parallel to the corresponding air flow, in which case angle α=0°. From this, the control dampers can be turned in one direction, whereupon angle α approaches the angle α=+G of the first closed position, or in the other direction, whereupon the angle α approaches the angle α=-G (i.e.=H) of the other closed position. 
     The apparatus according to FIG. 2 as a whole thus functions as follows: 
     In the position which closes air flows 37a-c, 42, all the control dampers 31a-c, 38 are in the fully closed position α=+G preferably 45°; 
     when the control levers 33 are turned to the position 45° or over some other structural angle, the other control dampers 31a-c, with the exception of the control damper 38 of the so-called bypass duct (still fully closed, α=+G) are fully open (α=O); 
     when the control levers 33 are turned further over the same 45° or an angle according to some other corresponding structural dimension (thus, for example, in total 0°-&gt;90°), the other control dampers 31a-c move further to the other fully closed position (α=-G=H) and the control damper 38 of the bypass duct opens into the fully open position (α=O). 
     The closing and control dampers are sealed against the partitions 43 and respectively end walls 44 either by means of sealing flanges or sealing strips 36 and against the side walls 45 by means of sealing flanges or sealing strips 32. A spring 34 or a counterweight ensures that the control damper of the bypass duct remains closed and is air-tight. 
     The control and closing dampers are turned by mediation of shafts 46 rigidly fastened to the levers 33, each damper turning about its own shaft 46. The opposite ends of the levers 33 are mounted with bearings 60 to a bar 47 of its articulation part 48. A drive device such as a motor 35 is attached to one of the shafts 46 to rotate the said shaft. Through the transmission of the bar 47 also the other shafts 46 mounted with lever 33 to the bar 47 also rotate in the corresponding manner. If the lever 33 is mounted on bearings to the articulation part 48, which for its part is fastened to the bar 47 with a clearance, for example by mediation of a groove 49 in it and a pin 50 in the bar 47, fitted in the groove, the damper 38 on the shaft in question turns only over the extent of that movement of the bar 47 which extends beyond the clearance. In this manner a phase difference is accomplished between the movement of the damper 38 and the movement of the other dampers 31a-c. In the embodiment of FIG. 2, the phase difference or lag is of the magnitude of angle G (i.e. preferably 45°). 
     Preferably the shafts 46 are located in the middle of the dampers 31 or respectively 38, transversely in relation to the flow, to minimize the moment produce by the flow. 
     When the control and closing device is applied to the heat recovery unit of ventilation, the unit comprising a plate heat exchanger operating according to the cross flow principle, and its bypass duct, two control and closing devices described above (FIG. 2) are used. This control and closing device unit is shown in FIGS. 3-6. For the sake of clarity, only the control and closing devices are shown in FIGS. 3-6, but the heat exchanger and other conventional components are not shown in FIGS. 3-6. 
     FIG. 3 depicts a situation in which the air conditioning plant is stopped and the control and closing device is closing the flows of both exhaust air and incoming air. All control dampers 51a-c, 61a-c, 58, 68 are in their fully closed positions. 
     FIG. 4 depicts a situation in which the air conditioning plant is in operation and the exhaust air P and the incoming air T are flowing through the heat exchanger. The control dampers 51a-c, 61a-c located at the heat exchanger are in their fully open position and the control dampers 58, 68 at the bypass duct are in their fully closed position, thereby closing the bypass-flow duct. 
     FIG. 5 depicts a situation in which the air conditioning plant is in operation and exhaust air P is flowing through the heat exchanger and incoming air T is flowing through the bypass duct of the heat exchanger. The exhaust-air control dampers 61a-c at the heat exchanger are in their fully open position and the exhaust-air control damper 68 at the bypass duct is in its fully closed position. The inlet air control dampers 51a-c at the heat exchanger are in their fully closed position and the inlet-air control damper 58 at the bypass duct is in its fully open position. 
     FIG. 6 depicts a situation in which the air conditioning plant is not taking in fresh air. At the heat exchanger all the control dampers 51a-c, 58 for inlet air T are in their fully closed position. At the heat exchanger the control dampers 61a-c for exhaust air P are in their fully closed position and at the bypass duct the exhaust-air control damper 68 is in its fully open position. The air conditioning plant is in this case in circulation-air use. 
     The control and closing device is, of course, suitable for use also in other than air conditioning plants as a device for dividing gas flows and as a bypass, control and closing device in various apparatus. 
     Depending on the use, there may be two, three, four or more control and closing ducts. The angle of movement of the control and closing dampers can be selected according to the situation, in which case angle G, i.e. the angel between the fully closed position and the fully open position, may at its smallest be only a few degrees and at its largest 90°. At its most advantageous angle it is within the range 30°-60°, and specifically 45°. The angle between the fully closed positions is typically double the above-mentioned angle, i.e. 2×G in which case angle G≠angle H. 
     It can, however, be brought that the movement on the two sides of the open position would be asymmetrical or that the closing in one direction would take place against a separate flange, in a manner different from that in the other direction, in which case angle G=angle H and the angle between the fully closed positions would be G+H. 
     The lever mechanism can also be designed according to need by using various lever and camshaft mechanisms to connect the levers 33 to each other and to the drive apparatus. By applying both an asymmetrical movement or closing of the damper and various lever mechanisms the control and closing device can be made to perform even complicated control functions with only one drive device or with a considerably smaller number of drive devices, and simpler device devices, then is conventional.